Plate type heat exchanger

ABSTRACT

A plate type heat exchanger includes a large number of plates formed by arranging plates each having concave and convex portions parallel to each other; and a large number of spacers sandwiched between the large number of plates, wherein the spacers include first spacers which are disposed on edges of a plate surface of the plate with a predetermined distance therebetween form a first flow passage in cooperation with the plate surface; and second spacers which are disposed on edges of a plate surface of the plate with a predetermined distance therebetween form a second flow passage having an inlet and an outlet which differ in direction from the first flow passage in cooperation with the plate surface, and the first spacers and the second spacers are alternately arranged between the large number of plates.

TECHNICAL FIELD

The present invention relates to a plate type heat exchanger whichperforms heat exchange between fluids.

BACKGROUND ART

As heat exchangers which perform heat exchange between fluids, therehave been known a tube type heat exchanger and a plate type heatexchanger, and these heat exchangers are applicable to many fluids. Thetube type heat exchanger is of a type where heat exchange is performedbetween fluids which flow inside and outside tubes. In the tube typeheat exchanger, a high pressure fluid is made to flow in the inside ofthe tubes and a low pressure fluid is made to flow outside the tubes andhence, the fluid can be used in the form of the high pressure fluid.However, a heat transfer area is limited to surfaces of the tubes andhence, the number of tubes is large whereby a volume and a weight of thetube type heat exchanger become large.

On the other hand, the plate type heat exchanger is of a type where heatexchange is performed by making fluids flow along both surfaces of aplanar plate respectively. Although the plate type heat exchanger can bemade light-weighted and compact, the plate type heat exchanger possessesa limited resistance against pressure and hence, the development of alarge-sized heat exchanger is difficult. Further, an inlet and an outletof the plate type heat exchanger are formed on a stacked plate surface(heat transfer surface) in general. Accordingly, when areas for formingthe inlet and the outlet are increased, a heat transfer area isdecreased so that there exists a drawback that heat exchange ability islowered.

Further, in the conventional plate heat exchanger, a pressure of fluidwhich acts on the plate surface is received by support plates on bothsides so that there exists a drawback that it is inevitably necessary toincrease a thickness of the support plate as an area of the plate isincreased.

Still further, a fluid on a heating side or a cooling side is taken intothis heat exchange system from the outside of the system and hence,there is a possibility that the fluid contains various kinds ofcontaminants. Such contaminants adhere to a heat transfer surface andbecomes a factor which causes lowering of heat transfer performance.Accordingly, there has been a request for a structure where a heattransfer surface can be cleaned.

CITATION LIST Patent Literature

PTL 1: Japanese Patent 3445387

PTL 2: JP-A-2015-49037

SUMMARY OF INVENTION Technical Problem

The present invention has been made in view of the above-mentioneddrawbacks, and it is an object of the present invention to provide aplate type heat exchanger which can maintain high heat transferefficiency, can be cleaned easily and can be made compact inconfiguration by making an inlet and an outlet for at least one fluidlarge while allowing a heat transfer surface to maintain a large area.

Solution to Problem

To overcome the above-mentioned drawbacks, the inventors of the presentinvention have made extensive studies to develop a heat exchanger whichallows a heat transfer surface to maintain a large area, enables aninlet and an outlet for at least one fluid to have a large area, enablesopen cleaning of at least one heat transfer surface, and can bemanufactured by press working for realizing the reduction of amanufacturing cost. As a result of such extensive studies, the inventorshave found that the above-mentioned drawbacks can be overcome byarranging different spacers alternately between a large number ofpress-formed plates on which concave and convex portions are formed bypress working thus forming inlets and outlets and flow passages forfluids in two directions, and the inventors have completed the presentinvention.

That is, the present invention provides [1] a plate type heat exchangerwhich includes: a large number of plates formed by arranging plates eachhaving concave and convex portions parallel to each other; and a largenumber of spacers sandwiched between the large number of plates, whereinthe spacers include: first spacers where the first spacers which aredisposed on edges of a plate surface of the plate with a predetermineddistance therebetween form a first flow passage in cooperation with theplate surface; and second spacers where the second spacers which aredisposed on edges of a plate surface of the plate with a predetermineddistance therebetween form a second flow passage having an inlet and anoutlet which differ in direction from an inlet and an outlet of thefirst flow passage in cooperation with the plate surface, and the firstspacers and the second spacers are alternately arranged between thelarge number of plates.

[2] The present invention is also characterized in that, in the platetype heat exchanger having the configuration described in [1], the inletand the outlet of the second flow passage are arranged orthogonal to aninlet and an outlet of the first flow passage.

[3] The present invention is also characterized in that, in the platetype heat exchanger having the configuration described in [2], the firstspacer is formed of a pair of L-shaped spacers arranged at corners ofthe plate surface in an opposedly facing manner and the second spacer isformed of a pair of straight-line spacers arranged in an extendingmanner on both edges of the plate surface parallel to each other.

[4] The present invention is also characterized in that, in the platetype heat exchanger having the configuration described in any one of [1]to [3], the plate is a press-formed plate on which the concave andconvex portions are formed by press working.

[5] The present invention is also characterized in that, in the platetype heat exchanger having the configuration described in any one of [1]to [4], the concave and convex portions formed on the plate are formedof: cylindrical concave and convex portions formed on a center portionof the plate;

and dotted concave and convex portions formed on the plate on both sidesof the center portion in an axial direction of the cylindrical concaveand convex portions.

[6] The present invention is also characterized in that, in the platetype heat exchanger having the configuration described in any one of [1]to [5], the convex portions formed on one plate and a flat surfaceportion of another plate disposed adjacently to the plate on which theconvex portions are formed are joined to each other.

[7] The present invention is also characterized in that, in the platetype heat exchanger having the configuration described in any one of [1]to [6], a large number of integral type heat transfer plates arearranged parallel to each other, wherein the integral type heat transferplate is formed such that the first spacers or the second spacers aresandwiched between two plates, two plates are formed into an integralbody by joining the convex portions formed on one plate and the flatsurface portion of the other plate to each other, and the second spacersor the first spacers are disposed on both outer side surfaces of the twoplates.

[8] The present invention is also characterized in that, in the platetype heat exchanger having the configuration described in [7], a largenumber of integral type heat transfer plates are arranged parallel toeach other, wherein the integral type heat transfer plate is formed suchthat L-shape spacers are sandwiched between two plates, andstraight-line spacers are formed on both outer side surfaces of the twoplates.

[9] The present invention is also characterized in that, in the platetype heat exchanger having the configuration described in any one of [1]to [8], a liquid pool is disposed below the plates.

The present invention also provides [10] an integral type heat transferplate which is the heat transfer plate used in the plate type heatexchanger described in any one of [1] to [9], wherein the integral typeheat transfer plate is formed such that the first spacers or the secondspacers are sandwiched between two plates, two plates are formed into anintegral body by joining the convex portions formed on one plate and theflat surface portion of the other plate to each other, and the secondspacers or the first spacers are disposed on both outer side surfaces ofthe two plates.

[11] The present invention is also characterized in that, in theintegral type heat transfer having the configuration described in [10],L-shaped spacers are sandwiched between two plates, and straight-linespacers are disposed on both outer side surfaces of the two plates.

Advantageous Effects of Invention

According to the plate type heat exchanger of the present invention, theinlet and the outlet for at least one of fluids can be made large whileallowing a heat transfer surface to maintain a large area and hence, ahigh heat transfer efficiency can be maintained. Further, the platesurface can be cleaned easily, and the plate type heat exchanger can bealso formed in a compact shape.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a perspective view showing the schematic configuration of aplate type heat exchanger according to one embodiment of the presentinvention.

FIG. 2 is a perspective view showing a state where 200 pieces ofpress-formed plates of the plate type heat exchanger according to oneembodiment of the present invention are combined with each other.

FIG. 3 is a view showing the schematic configuration of the press-formedplate.

FIG. 4 is a view showing a state where L-shaped spacers are disposed onone heat transfer surface of the press-formed plate.

FIG. 5 is a view showing a state where another plate is combined infront of the press-formed plate shown in FIG. 4.

FIG. 6 is a perspective view showing the schematic configuration of aplate type heat exchanger according to another embodiment of the presentinvention.

DESCRIPTION OF EMBODIMENTS

A plate type heat exchanger according to the present invention is notparticularly limited provided that the plate type heat exchanger is aplate type heat exchanger which includes: a large number of platesformed by arranging plates each having concave and convex portionsparallel to each other; and a large number of spacers sandwiched betweenthe large number of plates, wherein the spacers include: first spacerswhere the first spacers which are disposed on edges of a plate surfaceof the plate with a predetermined distance therebetween form a firstflow passage in cooperation with the plate surface; and second spacerswhere the second spacers which are disposed on edges of a plate surfaceof the plate with a predetermined distance therebetween form a secondflow passage having an inlet and an outlet which differ in directionfrom the first flow passage in cooperation with the plate surface, andthe first spacers and the second spacers are alternately arrangedbetween the large number of plates. The plate type heat exchangeraccording to the present invention exhibits various functionscorresponding to fluids to be used. For example, the plate type heatexchanger according to the present invention can be preferably used asan evaporator for water, a condenser for water or a heat exchangerbetween a high temperature gas and air.

Hereinafter, respective constitutional elements of the plate type heatexchanger are specifically described.

[Plate]

The plate according to the present invention is formed of a materialhaving high heat transfer property. One surface of the plate forms afirst heat transfer surface with which a first fluid is brought intocontact, and the other surface of the plate forms a second heat transfersurface with which a second fluid is brought into contact. Concave andconvex portions are formed on the heat transfer surfaces for allowingthe plate to secure heat transfer efficiency.

As the shape of the plate, a plate-like member having a quadrangularshape such as a square shape or a rectangular shape may be exemplified.When the plate is a rectangular plate, usually, the plates are arrangedparallel to each other in a horizontal direction while erecting longsides of each plate in a vertical direction. However, the plates may bearranged such that the plates are stacked in a horizontal direction.

The number of pieces of plates which are arranged parallel to each othercan be suitably adjusted to an extent that a heat transfer area can besufficiently ensured depending on use, application or the like. In thepresent invention, a large number of plates can be arranged. Forexample, the number of pieces of plates may be set to 200 or more.Further, the number of pieces of plates may be set to 1000 or more. As amethod of arranging the plates parallel to each other, usually, theplates are arranged such that convex portions (or concave portions) ofthe plates are directed in the same direction. However, the plates maybe arranged such that the convex portions (or the concave portions) aredirected in different directions.

It is preferable that the concave and convex portions formed on theplate according to the present invention be formed by press working.With such forming by press working, the plate having the concave andconvex portions can be manufactured at a low cost.

The concave and convex portions formed on the plate according to thepresent invention may be formed on at least a portion of each plate, andmay preferably be formed over the entire surface of a heat transfersurface of each plate. Although the concave and convex portions may beformed in any shapes, for example, dotted concave and convex portions orcylindrical concave and convex portions can be named. The dotted concaveand convex portions can be arranged in a matrix, for example. As aspecific shape of the dotted concave and convex portions, shapes such asa cubic, rectangular parallelepiped or semispherical shape can be named.

Cylindrical concave and convex portions can be formed on the plate inplace of the dotted concave and convex portions. In this case, it ispreferable that the cylindrical concave and convex portions be formed ona center portion of the plate, and the dotted concave and convexportions be formed on the plate on both sides of the center portion inan axial direction of the cylindrical concave and convex portions. Withsuch a configuration, a fluid which passes through the flow passage canbe effectively guided and, at the same time, a contact area between thefluid and the plate can be enlarged so that a heat transfer effect canbe enhanced. With respect to the cylindrical concave and convexportions, to ensure the smooth flow of a fluid, it is preferable toadjust a length of the cylindrical concave and convex portions at thecenter portion so as to prevent the cylindrical concave and convexportions from being present in the inlet and the outlet for a fluidformed by the L-shaped spacers (see FIG. 4). That is, the dotted concaveand convex portions are formed in the vicinity of the inlet and theoutlet for a fluid, and the cylindrical concave and convex portions areformed at an intermediate portion.

It is preferable that the plates according to the present invention beconfigured such that the dotted convex portions formed on the platerotated by 180° (upside down) be brought into contact with a flatsurface portion of the non-rotated plate disposed adjacently to therotated plate. That is, for example, when the dotted convex portions areformed on the plate in a matrix array, it is preferable that the dottedconvex portions formed on the rotated plate be displaced from the dottedconvex portions formed on the non-rotated plate by a half pitch byrotating the rotated plate by 180°. It is preferable that the dottedconvex portions and the flat surface portion be joined to each other byspot welding or the like. With such a configuration, it is possible toprovide the strong rigid structure which can sufficiently withstand apressure of a high-pressure fluid which flows through the flow passagesin the inside of the plate type heat exchanger. Accordingly, although aconventional plate type heat exchanger requires support plates having alarge thickness which support the plate from both sides, in the presentinvention, a thickness of the support plate can be reduced so that theplate type heat exchanger per se can be made light-weighted and compact.As will be described later, it is preferable that the integral heattransfer plates each of which is formed by joining two plates by spotwelding or the like be arranged parallel to each other.

Bolt through holes are formed in a periphery of each plate. A largenumber of plates are fixed to each other into an integral body bymounting assembling bolts in the bolt through holes. By bringing about astate where the assembling bolt is mounted in only one of four cornersof the respective plates, the respective plates are rotatable about theassembling bolt which functions as a rotary axis and hence, the heattransfer surface can be easily exposed to the outside whereby the heattransfer surfaces of the plate type heat exchanger can be easilycleaned. That is, a fluid which functions as a heat source of a heatexchanger, for example, geothermal hot water, hot spring water, abiomass burnt gas, a garbage burnt gas or the like containscontaminants. Such contaminants adhere to a surface of the heat transferplate and become a factor which impairs the heat transfer. With theabove-mentioned configuration, it is possible to periodically wash awaysuch an adhered material. Also with respect to the integral type heattransfer plate formed of two plates, the surfaces of the plates whichare not joined are in an exposed state so that these surfaces can beeasily cleaned.

[Spacer]

The spacers include: first spacers where the first spacers which aredisposed on edges of a plate surface of the plate with a predetermineddistance therebetween form a first flow passage in cooperation with theplate surface; and second spacers where the second spacers which aredisposed on edges of a plate surface of the plate with a predetermineddistance therebetween form a second flow passage having an inlet and anoutlet which differ in direction from the first flow passage incooperation with the plate surface, and the first spacers and the secondspacers are alternately arranged between the large number of plates.

As the first spacers and the second spacers, for example, a pair ofL-shaped spacers arranged in an opposedly facing manner at corners ofthe plate surface and a pair of straight-line spacers arranged in anextending manner on both edges of the plate surface parallel to eachother are named. That is, a thin space is formed by the opposedly facingsurfaces of the plates and the opposedly facing inner side surfaces ofthe spacers and, at the same time, portions (two portions) where thespacers are not present form the inlet and the outlet thus forming aflow passage.

In the plate type heat exchanger according to the present invention, thefirst flow passage having the inlet and the outlet and the second flowpassage having the inlet and the outlet whose directions are differentfrom the directions of the inlet and the outlet of the first flowpassage are formed by alternately arranging one kind or two kinds ofspacers. It is preferable that the inlet and the outlet of the firstflow passage be orthogonal to the inlet and the outlet of the secondflow passage. To be more specific, it is preferable that the firstspacer be formed of a pair of L-shaped spacers arranged in an opposedlyfacing manner at corners of the plate surface, and the second spacers beformed of a pair of straight-line spacers arranged in an extendingmanner on both edges of the plate surface parallel to each other.

For example, by forming the first L-shaped spacers on the corners of theplate surface (see FIG. 4), the inlet and the outlet (511, 521) areformed in the lateral direction and, at the same time, the first flowpassage having a zigzag shape is formed on the plate. A first fluid (forexample, compressed air having a low temperature) flows through thefirst flow passage. Heat energy of a second fluid having a hightemperature which flows through the second flow passage disposedadjacently to the first flow passage is propagated to a heat transfersurface which forms the first flow passage. Accordingly, when the firstfluid having a temperature of approximately 30° C., for example, flowsinto the first flow passage from an inlet duct, the first fluid passesthrough the first flow passage, and is discharged from an outlet duct ina state where the first fluid is heated to approximately 500° C.

By forming the second straight-line spacers on the edges of the platesurface in a vertical direction (up and down direction) (see FIG. 2),the inlet and the outlet are formed in the longitudinal direction and,at the same time, the second flow passage is formed in the verticaldirection of the plate. Heat energy of a second fluid (for example, ahigh temperature gas) which flows through the second flow passage ispropagated to the first flow passage through the heat transfer surface.Accordingly, when the second fluid having a temperature of approximately800° C., for example, flows into the second flow passage from the inletduct, the second fluid passes through the second flow passage, and isdischarged from the outlet duct in a state where the second fluid iscooled to approximately 500° C.

Opening areas of the inlets and the outlets of the first and second flowpassages can be decided by suitably adjusting thicknesses of the spacersand the numbers of the plates. Particularly, the inlet and the outlet ona side where the straight line spacers are formed can be made large insize.

It is preferable that the spacers be respectively formed of a materialhaving gas tightness to an extent that leakage of a fluid is prevented,a proper strength necessary for forming a casing of the plate type heatexchanger in cooperation with the plates, and heat insulation propertyto an extent that heat is not discharged to the outside of the heatexchanger.

[Integral Type Heat Transfer Plate]

It is preferable that the large number of plates (a group of plates)according to the present invention be configured such that a largenumber of integral type heat transfer plates are arranged parallel toeach other, wherein the integral type heat transfer plate is formed suchthat the first spacers or the second spacers are sandwiched between twoplates, two plates are formed into an integral body by joining theconvex portions formed on one plate and the flat surface portion of theother plate to each other, and the second spacers or the first spacersare disposed on both outer side surfaces of the two plates.Particularly, it is preferable that a large number of integral type heattransfer plates be arranged parallel to each other, wherein the integraltype heat transfer plate be formed such that L-shape spacers aresandwiched between two plates, and straight-line spacers are formed onboth outer side surfaces of the two plates. With such configurations, ahigh pressure fluid is allowed to flow through the flow passage formedbetween the joined plate surfaces, and the surfaces which are not joinedcan be brought into an exposed state so that these surfaces can beeasily cleaned.

[Liquid Pool]

It is preferable that in the plate type heat exchanger according to thepresent invention, a liquid pool be disposed below the plates. With sucha configuration, an amount of liquid generated in the plate portion canbe reduced so that the reduction of an area which functions as a heattransfer surface is prevented whereby lowering of a heat transfer effectcan be prevented.

For example, in a heat exchanger where evaporation and condensing takeplace, in the case of water, a change in volume between liquid and vaporis increased approximately 1000 times. When such a change in volumeoccurs, it is necessary for a flow passage to secure a sufficientcross-sectional area. However, a cross-sectional area of a plate heatexchanger is fixed and hence, the cross-sectional area is usuallydesigned with reference to vapor having a large volume. To consider thecase of a condenser, vapor which enters the condenser from above isgradually condensed so that the vapor is transformed into liquid. Whenthe liquid is pooled in a lower portion of the condenser so that aliquid surface is elevated, a heat transfer area used for condensing isdecreased so that condensing ability is lowered. Accordingly, by forminga liquid pool below the plate, it is possible to prevent the decrease ofa heat transfer surface caused by the elevation of the liquid surface.

In the evaporator, a liquid is elevated from below and a temperatureboundary layer develops along heat transfer surfaces on both sides. Itis estimated that evaporation progresses along with the elevation of theliquid. A height at which the liquid surface rises with respect to aheight of the heat transfer surface of the heat exchanger in thisevaporation step is basic information for estimating a heat transferstate and hence, it is often the case where the height is measured. Incase of the evaporator, a latent heat ratio is approximately 10 to 20%and hence, it is necessary to perform a control such that approximately20 to 30% of a heat transfer area is brought into contact with a liquid.By providing the liquid pool below the plate, the water level can bemaintained. Accordingly, a pressure and a flow rate of the fluid can becontrolled in accordance with a rotational speed of a water supply pumpand the degree of opening of a flow rate control valve.

As has been described above, the plate type heat exchanger according tothe present invention has the structure which enables the plate typeheat exchanger to maintain high heat transfer efficiency, to be cleanedeasily and to be made compact in configuration by making an inlet and anoutlet for at least one fluid large while allowing a heat transfersurface to maintain a large area.

That is, with the structure where the inlet and the outlet are formed onthe side surfaces of the plate by the spacers of the present invention,areas of the inlet and the outlet for at least one fluid can beincreased without decreasing a heat transfer area. For example, in thecase of condensing water, an area of the inlet for vapor can beincreased and hence, a flow speed of vapor having a large volume beforecondensing can be suppressed so that a pressure loss can be suppressed.Areas of the inlet and the outlet can be increased along with theincrease of the number of plates and hence, unlike a conventional platetype heat exchanger, there is no limit in the number of plates to beused so that a volume of the heat exchanger can be easily increased.Accordingly, it is possible to provide a plate type heat exchangerhaving high general-purpose-use property. Particularly, the flowpassages are formed by combining the first and second spacers havingdifferent shapes and hence, the flow passages can be easily changedcorresponding to a usage or an application.

Hereinafter, a specific embodiment of the above-mentioned plate typeheat exchanger is described with reference to drawings. FIG. 1 is aperspective view showing the schematic configuration of a plate typeheat exchanger according to one embodiment of the present invention.FIG. 2 is a perspective view showing a state where 200 pieces ofpress-formed plates of the plate type heat exchanger according to oneembodiment of the present invention are combined with each other. FIG. 3is a view showing the schematic configuration of the press-formed plate.FIG. 4 is a view showing a state where L-shaped spacers are disposed onone heat transfer surface of the press-formed plate. FIG. 5 is a viewshowing a state where another plate is combined in front of thepress-formed plate shown in FIG. 4.

As shown in FIG. 1 and FIG. 2, the plate type heat exchanger 10according to this embodiment (hereinafter simply referred to as “heatexchanger”) is formed by arranging a large number of press-formed plates100 formed by press working parallel to each other (see FIG. 2). Asshown in FIG. 3, bolt through holes 140 are formed in an outerperipheral portion of the press-formed plate 100. As shown in FIG. 1,assembling bolts 400 for fixing the large number of press-formed plates100 arranged parallel to each other are made to pass through these boltthrough holes 140. For example, a large number of, for example,approximately 200 pieces of press-formed plates are fixed to each otherin a parallelly arranged state. A side plate 600 is disposed on bothsides of the assembled press-formed plates 100 respectively.

Between the press-formed plates, L-shaped spacers (first spacers) 200(see FIG. 4) and straight-line spacers (second spacers) 300 (see FIG. 2)are alternately sandwiched. As shown in FIG. 1, an inlet duct 510 and anoutlet duct 520 of a first flow passage formed by plate surfaces and theL-shaped spacers 200 are disposed on upper and lower portions of sidesurface portions of the heat exchanger 10 respectively, and an inletduct 530 and an outlet duct 540 of a second flow passage formed by platesurfaces and the straight-line spacers 300 are disposed on upper andlower portions of the heat exchanger 10 respectively. Opening areas ofthese inlets and outlets 510,520,530,540 are decided in accordance withthe number of plates 100.

As shown in FIG. 3 and FIG. 4, the press-formed plate 100 is arectangular planar plate having a longitudinal size of approximately 2 mand a lateral size of approximately 1 m, for example. A plurality ofsemispherical concave and convex portions 120 having a diameter ofapproximately 5 cm are formed and arranged on both upper and lower sidesof the planar plate in a matrix array. Cylindrical concave and convexportions 130 having a length of approximately 75 cm are formed on acenter portion of the press-formed plate 100 such that the cylindricalconcave and convex portions 130 are prevented from being present at theinlet 511 and the outlet 521 of the first flow passage.

Although these press-formed plates 100 are arranged such that thesemispherical convex portions are directed in one direction, thepress-formed plates 100 are arranged in such a manner that every otherpress-formed plate 100 is rotated upside down by 180°. That is, as shownin FIG. 3, a larger space is formed on a left side than on a right sidein the drawing so that when the press-formed plates 100 are combinedwith each other while rotating one press-formed plate 100 from anotherpress-formed plate 100 by 180°, the semispherical convex portions andflat surface portions disposed between the semispherical convex portionsare brought into contact with each other. By joining the convex portionsand the flat surface portions to each other, an integral heat transferplate formed of two press-formed plates 100 is formed. As shown in FIG.4 and FIG. 5, in this integral heat transfer plate, the L-shaped spacers200 are sandwiched between two plates, and the straight-line spacers 300are disposed on both outer side surfaces of the two plates. Accordingly,such an integral heat transfer plate forms an integral type heattransfer plate. A large number of this integral type heat transferplates are arranged parallel to each other.

As shown in FIG. 4, the L-shaped spacer 200 is arranged on a left uppercorner and a right lower corner of a heat transfer surface of thepress-formed plate 100 respectively. On the other hand, as shown in FIG.2, the straight-line spacer 300 is arranged on both edges of the heattransfer surface of the plate 100 in an erected state respectively in astate where the straight-line spacers 300 extend in a verticaldirection. The L-shaped spacers 200 and the straight-line spacers 300are arranged alternately between the press-formed plates 100.

In the plate type heat exchanger 10 having the above-mentionedconfiguration, for example, compressed air having a temperature ofapproximately 30° C. flows into the plate type heat exchanger 10 fromthe first inlet duct 510 as a first fluid. Compressed air passes throughthe first flow passage and is discharged from the first outlet duct 520.On the other hand, a high temperature gas having a temperature ofapproximately 750° C. flows into the plate type heat exchanger 10 fromthe second inlet duct 520 as a second fluid. The high temperature gasrises through the second flow passage and is discharged from the secondoutlet duct 540. With such a process, a heat exchange is performed inthe plate type heat exchanger 10 so that a high temperature gas having atemperature of 750° C. is cooled down to 500° C. and, at the same time,compressed air having a temperature of 30° C. is heated to 500° C.

Next, a plate type heat exchanger according to another embodiment of thepresent invention is described (see FIG. 6). The plate type heatexchanger according to this embodiment is characterized in that flanges550 to 580 for mounting the plate type heat exchanger to an outsideequipment are provided to inlet and outlet ducts 510 to 540 for fluids.The plate type heat exchanger according to this embodiment issubstantially equal to the plate type heat exchanger according to theabove-mentioned one embodiment with respect to the configurations otherthan the above-mentioned configuration.

INDUSTRIAL APPLICABILITY

The plate type heat exchanger according to the present invention isusefully employed by an evaporator, a condenser or the like of a waterbinary cycle power generation system so that the plate type heatexchanger has high industrial usefulness.

REFERENCE SIGNS LIST

10: plate type heat exchanger

10A: plate type heat exchanger

100: press-formed plate

105: first heat transfer surface

110: second heat transfer surface

120: semispherical concave portion

130: circular cylindrical concave and convex portions

140: bolt through hole

200: L-shaped spacer (first spacer)

300: straight-line spacer (second spacer)

400: assembling bolt

510: inlet duct of first flow passage

511: inlet of first flow passage

520: outlet duct of first flow passage

521: outlet of first flow passage

530: inlet duct of second flow passage

540: outlet duct of second flow passage

550: inlet flange

560: outlet flange

570: inlet flange

580: outlet flange

600: side plate (support plate)

1. A plate type heat exchanger comprising: a large number of platesformed by arranging plates each having concave and convex portionsparallel to each other; and a large number of spacers sandwiched betweenthe large number of plates, wherein the spacers include: first spacerswhere the first spacers which are disposed on edges of a plate surfaceof the plate with a predetermined distance therebetween form a firstflow passage in cooperation with the plate surface; and second spacerswhere the second spacers which are disposed on edges of a plate surfaceof the plate with a predetermined distance therebetween form a secondflow passage having an inlet and an outlet which differ in directionfrom an inlet and an outlet of the first flow passage in cooperationwith the plate surface, and the first spacers and the second spacers arealternately arranged between the large number of plates.
 2. The platetype heat exchanger according to claim 1, wherein the inlet and theoutlet of the second flow passage are arranged orthogonal to an inletand an outlet of the first flow passage.
 3. The plate type heatexchanger according to claim 2, wherein the first spacer is formed of apair of L-shaped spacers arranged at corners of the plate surface in anopposedly facing manner and the second spacer is formed of a pair ofstraight-line spacers arranged in an extending manner on both edges ofthe plate surface parallel to each other.
 4. The plate type heatexchanger according to claim 1, wherein the plate is a press-formedplate on which the concave and convex portions are formed by pressworking.
 5. The plate type heat exchanger according to claim 1, whereinthe concave and convex portions formed on the plate are formed of:cylindrical concave and convex portions formed on a center portion ofthe plate; and dotted concave and convex portions formed on the plate onboth sides of the center portion in an axial direction of thecylindrical concave and convex portions.
 6. The plate type heatexchanger according to claim 1, wherein the convex portions formed onone plate and a flat surface portion of another plate disposedadjacently to the plate are joined to each other.
 7. The plate type heatexchanger according to claim 1, wherein a large number of integral typeheat transfer plates are arranged parallel to each other, wherein theintegral type heat transfer plate is formed such that the first spacersor the second spacers are sandwiched between two plates, two plates areformed into an integral body by joining the convex portions formed onone plate and the flat surface portion of the other plate to each other,and the second spacers or the first spacers are disposed on both outerside surfaces of the two plates.
 8. The plate type heat exchangeraccording to claim 7, wherein a large number of integral type heattransfer plates are arranged parallel to each other, wherein theintegral type heat transfer plate is formed such that L-shape spacersare sandwiched between two plates, and straight-line spacers are formedon both outer side surfaces of the two plates.
 9. The plate type heatexchanger according to claim 1, wherein a liquid pool is disposed belowthe plates.
 10. An integral type heat transfer plate which is the heattransfer plate used in the plate type heat exchanger described in claim1, wherein the integral type heat transfer plate is formed such that thefirst spacers or the second spacers are sandwiched between two plates,two plates are formed into an integral body by joining the convexportions formed on one plate and the flat surface portion of the otherplate to each other, and the second spacers or the first spacers aredisposed on both outer side surfaces of the two plates.
 11. The integraltype heat transfer plate according to claim 10, wherein L-shaped spacersare sandwiched between two plates, and straight-line spacers aredisposed on both outer side surfaces of the two plates.